chall



April 29, 1958 H. J. CHALL CALCULATING MACHINE '7 Sheets-Sheet 1 Filed May 17, 1955 JNVENTOR. HAROLD J. CHALL ATTORNEY Filed May 17, 1955 7 Sheets-Sheet 2 v INVENTOR.

HAROLD u. CHALL.

FIE E rm/awa A ril 29, 1958 H. J. CHALL 2,832,544

CALCULATING MACHINE Filed May 17, 1955 7 Sheets-Sheet 5 INVENTOR. HAROLD J. CHALL BY A 0),

ATTORNEY A ril 29, 1958 H. J. CHALL 2,8

CALCULATING MACHINE Filed May 17, 1955 7 Sheets-Sheet 4 H. J. CHALL CALCULATING MACHINE 1 April 29, 1958 7 Sheets-Sheet 5 Filed May 17, 1955 Von April 29, 1958 H. J. CHALL CALCULATING MACHINE Filed May 17. 1955 7 Sheets-Sheet 6 April 29, 1958 H. J. CHALL CALCULATING MACHINE 7 Sheets-Sheet 7 Filed y 17. 1955 won United States Patent CALCULATING MACHINE Harold J. Chall, San Leandro, Califi, assignor to Friden, Inc., a corporation of California Application May 17, 1955, Serial No. 509,022

13 Claims. (Cl. 235-137) This invention relates to a calculating machine, such as a listing adding machine, and more particularly to the accumulator and associated mechanism of such a machine, and is a continuation in part of my application Ser. No. 215,064, filed March 12, 1951, for calculating machine, and noW abandoned.

it is among the objects of the invention to provide in a calculating machine, such as a listing adding machine, an accumulator and associated mechanism wherein the accumulator is fixedly mounted on the machine base and has a rigid frame, and gears rotatable on shafts fixedly and rigidly supported by the frame; wherein the ordinally arranged accumulator gears are bi-directionally driven through individual drive gears and positive and negative transmission gear assemblies from the actuating sectors of the machine; wherein the positive and negative transmission gear assemblies are movable into, and out of, engagement with the drive gears of the fixedly mounted accumulator; wherein spring-actuated pawls are pivotally mounted on the accumulator frame, one pawl at each diametrically opposite side of each accumulator gear, and are effective, when released, to turn the coordinal accumulator gears one unit space in the corresponding positive or negative direction to accomplish tens-carry from one accumulator order to the next higher order; wherein positive stop means are provided to limit the operation of the pawls to one unit space movements of the corresponding accumulator gears and each pawl is provided with a gear engaging live tip so that a pawl can be withdrawn from its gear turning position without turning the associated gears in the opposite direction; wherein latches are pivotally mounted on the machine frame, one at each diametrically opposite side of each accumulator gear and are spring urged into engagement with the pawls on the corresponding sides of the gears to latch the pawls in inoperative position and tens-carry cams are mounted one on each accumulator gear and extend diametrically across the gears; wherein a live tip is provided on each latch and is engaged by the coordinal tens-carry cam when the associated accumulator gear has been turned ten h unit spaces from its position and the live tips are so mounted that when an accumulator gear is turning in one direction, the live tip on the latch at one side of the gear is effective to disengage the latch from the associated pawl, while the live tip on the latch at the opposite side of the gear by-passes the tens-carry cam without moving the associated latch and, when the gear is rotating in the opposite direction, the cam by-passes the live tip at the one side of the gear and acts on the live tip at the opposite side to move the latch to free the associated pawl; wherein a cam operated restore member, or bail, is provided and acts to first block the springactuated pawls while a tens-transfer is being set up so that the pawls can move to a latch free position but are restrained against movement to gear turning position, are

later freed to move to gear turning position and complete the tens-transfer and are afterward restored to latched Patented Apr. 29, 1958 condition and the restore member returned to blocking position.

it is also among the objects of the invention to provide an accumulator of the character indicated which is simple, compact and durable in construction, and has the same set of accumulator gears operative to receive both additive and subtractive values, and which can be installed in, and removed from, the associated machine as a completely assembled unit.

Other objects and advantages will become apparent from a consideration of the following description and the appended claims in conjunction With the accompanying drawings, wherein:

Fig. i is a side view of the adding and subtracting machine of my invention taken from the right, with the cover removed, and with certain parts, such as the controls, eliminated;

Fig. 2 is a side view of the mechanism of one order of my accumulator and actuator therefor;

Fig. 3 is also a side view of one order of the mechanism of my invention, showing particularly the actuator drive and the printing mechanism;

Fig. 4 is a cross-sectional view of the actuator shown in Fig. 3, taken along the planes indicated by the line 4-4 of Fig. 3;

Fig. 5 is a side view of another form of an actuator suitable for my invention;

Fig. 6 is a partial front view of the accumulator mechanism with the actuator and connective gearing removed, taken along the oblique planes indicated by the lines 66 of Fig. 2; and

Figs. 7, 8 and 9 are somewhat diagrammatic, left end elevational views showing the accumulator with certain parts omitted and the tens-carry operating mechanism in three successive operating positions.

The machine of the present invention is mounted in a suitable frame which may comprise a suitable base 36 (Fig. 1), frame plate 37, and auxiliary plate 33, the frame and auxiliary plates being tied together into a rigid unit by suitable tie rods 39 and spacing sleeves 46.

SELECTION MECHANISM The keyboard selection mechanism, including the setting pins and the diiferentially settahle arcuate racks, is substantially identical with the multiplication mechanism shown and described in the patent to Carl M. 'Friden, No. 2,371,752 issued March 20, 1945, to which patent reference is made for a more complete disclosure of this mechanism. The keyboard is of the type normally called a ten-key keyboard, as there is a single value selection key for the values 0 and l to 9, inclusive. In this type of keyboard, the value keys 34 are used to set a value in an order of a shiftable selection mechanism which is then shifted ordinally so that the same keys may be used to insert values into each order of the machine. In my preferred form, the keyboard and the associated selection levers are fixed in the machine, while the selection pins and differentially settable racks are mounted in a carriage shiftable in relation thereto. Preferably, the nine value keys of 1 to 9, inclusive, are arranged in a square 3 x 3 relation with a 0 key, not shown, located adjacent to the value keys. The key stems 291 of the value keys are bent, as fully shown and described in said patent, to form guide stems 203 directly underneath the key, and guide extensions 262 formed to lie in an echelon arrangement with respect to each other. The key stems are mounted in suitable plates 2% and 263-7 and the keys are maintained in an elevated position by suitable springs, not shown.

Associated with the value keys 34, are a series of selection levers 216 which, upon depression of the corresponding key, provide means for moving a selected pin 251, of the then aligned ordinal row of pins (in the carriage) to active position. A selection lever is provided for each one of the l to 8 keys 34, while a fixed stop, not shown, is used for the value of 9. Each lever 216 is provided with an arm 217 pivoted on a common transverse shaft 213, the series of arm 217 being disposed in adjacent lateral relationship in a comb plate 219. Each of the arms 217 is provided with an upwardly projecting abutment 221, the abutments being disposed in an aligned staggered, or echelon, relation corresponding to the similar relation of the extensions 262 of the value keys. Each selection lever 216 is provided at its lower end with an upwardly and rearwardly projecting pin setting finger 222 which extends through a suitable aperture in plate 219. It will be understood that the levers 216, which are in laterally adjacent relation ship in their upper portions, are bent so that their fingers 222 lie in a single ordinal plane. At the base of finger 222 each lever has a laterally projecting stop which normally seats against bracket 224, the lever being urge into contact therewith by a suitable spring 225.

In the preferred form of mechanism there is no selection lever 216 for the zero key, that key operating merely to shift the internal carriage a single space, or order, to the left. There is likewise no selection lever for the 9 key as operation of that key operates to release the spring-powered diiferential rack which is stopped by a fixed abutment rather than by a differentially placed pin 251, and to step the carriage one step to the left.

The selection mechanism is mounted in an internal carriage comprising end plates 231 held in spaced relationship by a pair of setting pin mounting plates 232 at the lower extremity thereof and a stop bar 268 in the upper portion. The end plates and intermediate structure are held as a rigid unit by suitable tie rods 235. The carriage assembly is adapted to slide along a pair of supporting rods 237. The carriage is normally in an extreme right-hand position from which it is urged by resilient means, such as a suitable spring, not shown. The carriage is moved stepwise to the left, order by order, with the insertion of each value into it by means described in said patent but not here shown, and is held in its adjusted position by a suitable ratchet means. The pin plates 232 are provided with a series of rows of aligned slots to receive the setting pins 251 for limited endwise sliding movement, as determined by spaced-apart pins 252 provided thereon, between the two plates. Below the lower plate 232 each pin 251 is provided with a slot, or aperture, 254- for use in restoring the pin to its lower inactive position, as shown in Fig. l. The up per ends of the pins are of varying length to allow for engaging the differentially settable arcuate racks 261 to block further clockwise rotation thereof. The respective setting pins 251 are lifted by rocking of the associated selection levers 216 and are held in their raised position by a suitable detent, not shown.

For each order of settable pins 251, the carriage is provided with a differentially settable element in the form of a pivoted, spring-actuated rack, or segment, 251. Each rack is normally held in its zero position from which it can be released to assume a differential adjustment in accordance with a pin of the associated row, which pin is moved to active position by depression of a selected value key. The rack segments are journalled on a common shaft 590. Each rack is provided with an ear 254 to which is attached one end of a suitable tension spring 265, the other end of which is fastened to the upper tie rod 235, thus urging the elements in a clockwise direction (Fig. 1) around their common shaft The forward portion of each rack 261 carries an indicating segment 35, upon which are fixed suitable numbers indicating the value placed in the keyboard, one value on the segment being viewable through a suitable window in the 4 cover of the machine. The back portion of each of these segments 261 carries a gear segment 266 having a plurality of gear teeth 257. The segments 261 are latched in their zero position by suitable pawls 269, urged counter-clockwise around a common tie rod 271 by suitable mugs, not shown.

l cans are provided for releasing the rack segments 261, the active order of the pin carriage, y rocking of the latch pawl member 269 clockwise simultaneously with the movement of a pin to active position. Pawl 252', for releasing the associated rack segment 261, is moved to a releasing position by means of a pawl reeased arm 276 pivoted at 277 to an adjacent supporting plate 37. The arm 276 carries an upper nose 278 ordinally aligned with the fingers 222 of arms 216, operative to set the ordinal selection pins. The arm 276 ally connected to a link 281, the upper end of 'hich is pivotally connected to a lever 282 pivoted at to the frame plate. The lever 282 carries a forwardly extending finger 284 which underlies a bar 22-6 mounted in a pair of rockable arms 287. The bar 286 is depressed by depression of any of the value keys, and such depression rocks the lever 232 (counter-clockwise in Fig. l), pulling the link 28?. upwardly to rock the lever 276 counter-clockwise. The rocking of the lever 2'76 counter-clockwise rocks the latching pawl 269 clockwise, thereby releasing the rack 261 associated therewith.

it is believed that the operation of the selection mechanism will be readily understood. Briefly, the depression of a key operates simultaneously to rock the associated 7 6 and the bar 286 which, in turn, rocks lever 282. Rocking of a lever 216 operates through its lower nose, or finger, 222 to move the associated pin 251 of the aligned order of the carriage to an elevated position. Simultaneously, the rocking of the lever 232 rocks arm 2'76 to release the latching pawl 269. Thereupon, the rack 261 is pulled by its spring 265 clockwise until stopped by the elevated pin 251, in which position it is locked by the pin. it will be recalled that the 9 key has no associated pin, merely operating to release the pawl the rack 261 being blocked by a fixed stop, not shown, in the carriage. Simultaneously, with the entry of a value into a differentially positionable rack 251, the carriage is given a single step to the left in order to bring the next order into alignment with the noses 222 and 278, whereupon a second digit can be set into the selection mechanism. In this manner the carriage is stepped to the left, and values entered into the selection segments, order by order. When a complete value has been inserted, the various selection segments, corresponding to the orders in that value, will have been rocked clockwise from their normal Zero position a differential amount.

t can also be mentioned that as the carriage is rcto d to the right by a suitable mechanism, not shown, the pins are restored to their normal lower position by a means not shown, but fully shown and described in the above-mentioned patent.

ACTUATOR The actuating mechanism, shown in Figs. 2 and 3, comprises a series of ordinally arranged actuator segments 1.1. suitably mounted on a transverse shaft 12 supported in the frame plates, there being one such actuator gear segment for each order of the accumulator, hereinafter described. The gear segments 11 are held in properly spaced relationship by a suitable comb 13, which nay also serve as a spacer for the frame plates 36 and or by the tenon and slot arrangement shown in Fig. l. in its normal inoperative position, the

segments 11 abut against a stop rod, or bar, 14. gear segments are provided with suitable gear teeth 15 as shown.

The actuator gear segments 11 are, during a portion of the operative cycle, connected to the diit'erentially set table racks 261 through a pendent gear train designated generally by the reference character 19. Each order of such gear train comprises suitable idler gears 20, 21 and 22 rotatably mounted on parallel shafts 23, 24 and 25, respectively. The three shafts are journalled in a rockable cradle 26 having a pair of parallel arms 2"!" connected by a bail 28. The shaft 23 is extended longitudinally through the cradle and through the frame plates 37 and 38 to form a pivot about which the cradle 26 may be rocked. The shaft 23 is so spaced with relation to the common shaft 12 of the gear segments it that gear and the actuator segment 11 are always in mesh.

Normally, the pendent gears are held in a neutral position in which the terminal gear 22 of the train is disengaged from the related selection segment 261 by a suitable centralizer mechanism such as that shown in Fig. l. A simple form of centralizer includes a pair of centralizer arms pivotally mounted on the extended shaft 23. The two arms 45 are resiliently urged together by a suitable spring 46 and bear against a stop pin 47 mounted on the auxiliary plate 38. The two arms 45 also bear against a pin 31 mounted in an extended arm 29 of righthand arm 27 of the cradle 26. It is thus apparent that, as the cradle is rocked in either direction around its pivot shaft 23, an arm 45 is pushed away from the stop pin at? by the pin 30, against the urgency of spring 46, the other arm being held by the stop pin 47. When the positive rocking force is removed from the cradle, it is obvious that it will be snapped back to its disengaged position by the spring 46.

it will be recalled that at the completion of the insertion of a value into the selection mechanism the various selection segments 261 into which values have been entered will have been rocked clockwise to a differential position. Then the plus or minus key, not shown, will be depressed to initiate a digitation cycle. At the start of the digitation cycle the pendent gear assembly 19 is rocked into engagement with the selection segment 261. This rocking of the pendent gear assembly is under the control of mechanism not here shown. The actuator gear segment 11 is then rocked (counter-clockwise in Figs. 2 and 3) to restore the selection segments to their normal 0 position. The actuator gears have a disengageable connection with a common operating bail 50 which is given an angular movement equivalent to the entry of a value of 9 into the selection segment 261. However, when the selection segment 261 abuts against the stop 268, rotation of the train of gears, including the actuator 11, the pendent gears of the assembly 19, and the selection segment 261, is stopped and the separable connection between the actuator gear 11 and the operating bail 50 is broken. In this manner, the selection se ments are restored to their Zero position in the first part of a digitation cycle and simultaneously the actuators have been rotated differentially an angular amount fixed by the selection segments. Therefore, at the end of the first part of a digitation cycle, the actuator segments 11 are differentially displaced an amount corresponding to the value set into the keyboard.

It can be noted here that the left-hand carriage frame plate 231 carries a bracket 331 (Fig. 2) which is provided with a laterally extending ear 332 aligned with the tooth of the selection segment which would mesh with gear 22 when the segment is in its 0, or home, position. This ear, or bail, 332 has a length corresponding to the width at the accumulator. Thus, when the pendent gear train ii@ is rocked into engagement with the selection segments 261i, those terminal gears 22 to the left of the highest order of the selection carriage are in mesh with the car 332. In this manner, those gears 22, which are to the left of the selection segments, are locked against operation during the digitation cycle.

Two forms of a preferred severable actuator drive are shown in the figures, one being shown in Figs. 3 and 4 and a second being shown in Fig. 5. In the form shown in Figs. 3 and 4, a pair of spring plates 51 are rotatably mounted on the shoulder of hub 16 of the actuator gear 11. The two spring plates are also mounted on a hub 58 which is rotatably mounted on the bail 50. The bail 5t) oscillates in a suitable slot 57 in the actuator gear 11. Thus, during oscillation of the bail 5%, the spring plates 51 oscillate with it as a unit. The actuator gear 11 is provided with an aperture 52 which embraces a ball 53. In the normal, or zero, position of the actuator gear 11 (the operatin bail 50 being in its full-cycle position) the ball so embraced by holes 54 properly located in the spring plates 51. Thus, as the bail 5b and spring leaves 51 move at the start of the digitation cycle, the ball 53 and holes 54 form a yieldable, or resilient, connection between the actuator gear 11 and the spring plates. in this manner, the gear 11, pendent gears 19, and the selection segment 261 are driven until the selection segments 261 abut the stop bar 268. Upon the selection segment 261 reaching its zero, or full-cycle, position, the spring plates 51 will give slightly to unseat the ball 53 from the holes 54. Thus, the operating bail 59 and spring leaves 51 are free to continue their full oscillation while the actuator gear 11 is held in the adjusted differential position. The connection between the operating bail and the actuator gear just described provides one of suitable strength to move the gear, pendent gears, and the selection segment and still provides a resilient drive that will stop the actuator without appreciable shock to the mechanism.

After the end of the downward stroke of the operator bail 5% there is a slight dwell of sufiicient length to permit the pendent gears 19 to be rocked out of engagement with the selection segment 261 and for the printing mechanism, to be described hereafter, to be operated. The gear trains from the actuator to the accumulator are then engaged so that the value differentially set in the actuator gear 11 may be additively or subtractively transferred to the accumulator, and thereafter the operating bail 59 returns to its full-cycle position. The friction between the spring leaves and the ball 53 may be sufiicient to restore the actuator gear to its full-cycle, or clockwise, position. However, in order to make the return of the actuator gear 11 positive in all respects, I prefer to mount a pin 55 between the spring leaves, and operating in the slot 5'? of the actuator gear, to .abut a shoulder 56 at one end of the slot and positively return the gear to its full-cycle position.

A second and somewhat preferred form of disengageable, or yieldable, drive for the actuator segment 11a is shown in Fig. 5. In this form of my invention, the segment is provided with a spacer hub 16, as before, adapted to be rotatably mounted on the shaft 12. The segment Illa is provided with an arcuate slot 57 of sufficient length to permit the bail to be rocked through its full stroke without moving the actuator. In this form, I prefer that the bail 50 be provided with a plurality of rollers 61 ordinally spaced therealong. Associated with the roller and hail is a bellcrank 62 pivotally mounted on the actuator gear 11a by any suitable means such as a rivet, or pin, 63. The bellcrank has a short arm 64 bent so that the end thereof lies within a slot 57 formed in the actuator gear. A suitable tension spring 66 has one end hooked through a suitable hole 67 formed in the actuator 11a, and the other end hooked over the hookshaped end 68 of the arm 64. A downwardly projecting arm 69 of the bellcrank has an arcuate shoulder 70 formed thereon adapted to engage the roller 61, the arm 69 being extended, as at 71, to provide an arcuate surface adapted to engage the roller 61 through the stroke of the actuator bail 50. The tension of the spring 66 and the shape of the shoulder 7% provide a severable connection of sufficient strength to rock the actuator gear 61 against the inertia of the pendent gears and the selection segment 261. However, when the selection segment 261 abuts its stop 268, bellcrank 62 will be cammed clockwise against the tension of its spring without appreciable shock to the mechanism. The bail and its associated roller 61 are therefore permitted to continue their full stroke without appreciable load on the drive mechanism.

PRINTING MECHANISM The mechanism of my invention is designed primarily for use with a printing mechanism adapted to print the various items and also to print totals and Subtotals. Such a printing mechanism is shown in Fig. 3, although any suitable form could be used. In each order of the machine, the printing mechanism will include a suitable idler ear 76 rotatably mounted on a common transverse shaft '77. The idler will be in mesh with the actuator 11 at all times through the first gear 20 of the pendent train. The idlergear 76 may engage a suitable printing wheel gear 78 which is rotatably mounted on a suitable pin, or shaft, 79, or the like. The shaft 79 is carried on a. pair of arms 80 which are rotatably mounted on a transverse shaft 31 so that the printing wheel gear 78 may be rocked into engagement with the idler 76 or disengaged there from. A printing wheel 82, provided with suitable printing type, is rigidly secured to the gear 7 8 so that the gear and printing wheel rotate as a unit. A suitable detent 83 is associated with each printing wheel to lock it against rotation when the printing wheel gear 78 is disengaged from the idler 76. Such a detent may include a suitable nose 87 adapted to engage between adjacent printing abutments, or type, on the printing wheel 32. The detent, shown in Fig. 3, is urged in a clockwise direction by a suitable tension spring 84 and is pivoted on a transverse shaft 235 secured to, and between, the arms 80. A transverse sto bar 86 is so located as to rock the detent out of engagement with the printing wheel when the printing wheel gear 78 is in mesh with the idler 76. However, upon rocking of the arms 80 to disengage the printing wheel '78 from the idler 76 the detent 33 is permitted to rock clockwise, so that the nose 87 thereof will engage between the adjacent type and therefore block rotation of the printing wheel 82. Printing may occur by conventional means which will rock the arms 80 with a hammer-like stroke during the period of dwell at the end of the first phase of the digitation cycle-substantially simultaneously with the disengagement of terminal gear 22 of the pendent train from the selection rack 2st above-mentioned, and after the actuating segments have moved to set the printing wheels and return the selection racks to their 0 positions.

ACCUMULATOR The accumulator mechanism of my invention is preferably mounted in a subframe assembly 90 comprising a plurality of spacing plates 91 each having an upper extension 92, as shown. The respective plates, preferably one for each order, are rigidly secured together by suitable tie rods 3, 94, 95, 5 6, 97, $8 and 99. The plates can be held in suitable spaced relationship by suitable spacers and also by means of a slotted cover plate, or comb, 1% and a base plate 101. The base plate is secured to each of the spacing plates by means of suitable machine screws 1G2 threaded into a common bar 193 extending through apertures 104 in the spacing plates adjacent the base plate, as shown in Fig. 2. This subframe is mounted on a base 36 by suitable bolts, or screws, not shown.

Mounted in the subframe 90 are a plurality of accumulator drive gears 11h, one for each order of the accumulator. These drive gears are rotatably mounted on a transverse shaft 111 carried by the spacing plates $1. Each gear is held in any adjusted position by a suitable detent 113 pivotally mounted on the tie rod 94 and springurged into engagement with the drive gear 116 by a suitable spring 114. The drive gear 116 is constantly in mesh with a coordinal ZO-tooth accumulator gear 115. The gears 115 are mounted on a common shaft 116 sult- Cir '\ ably journalled in the subframe 90. As shown in Fig. 2, a pair of diametrically opposed tens-transfer cams 117 are rigidly secured to each accumulator gear 115.

The subframe 90 is so mounted with respect to the actuator segments 11 that the drive gear 110 can become enmeshed with either the positive gear train or a negative gear train, both of which are in mesh with the actuator 11. The enmeshing of the plus or minus gear trains will take place during the period of dwell at the end of the downward stroke of the bail 50 above-mentioned, so that the accumulator gear 115 will be connected to the actuator it during the return stroke of the latter.

it will be obvious that two separate gear trains could be provided to selectively engage drive gear 110 upon the return stroke of the actuator, one having an odd number of gears for digitation in one direction and the other having an even number of gears for digitation in the op posite direction. However, it will be also obvious that the pendent gear train 19 can be used for one of the digitation gear trains, and this is the form shown in the drawings. Preferably, the pendent gear assembly 19 is used as the positive or additive gear connection, the cradle 26 being rocked to a second operative position in which the terminal gear 22 will mesh with the drive gear 11o. Thus, for additive operation, the pendent gear train 19 will be rocked from engagement with the selection segment 251 into engagement with the drive gear during the dwell at the end of the first, or setting, stroke of the actuator 11.

The negative gear train 120 is in many respects quite similar to the pendent gear train 19, except that it will have an even number of gears when the pendent gear train has an odd number. A cradle is formed by a pair of arms 121 pivoted to the frame plates 37 and 38 by any suitable means such as studs 12?. (see Fig. 3). The two arms 121 are interconnected by a pair of transverse shafts 123 and 124, on which shafts are mounted (in each order of the accumulator) a pair of gears 125 and 126, re spectively.

The controls of my machine (not shown in this application) will include means whereby either the pendent gear train 19 or the negative gear train 120 will be rocked into engagement with the drive gear at the end of the first downward movement of the bail 50. It is thus obvious that the values difierentially set in the actuator seg ments 11 will be transferred, additively or subtractively, to the drive gear 110 and thence into the accumulator gear 115 during the return stroke of the actuator segments 11, driven by the bail 50. Upon the return of the actuators 11 to their full-cycle position the cycle is completed, the tens-transfer operation occurring at the end of the stroke.

TENS-TRANSFER The tens-carry mechanism preferably is of the spring actuated type. In this form of transfer mechanism, the arrangement in each order is identical and there are two such mechanisms, one for a positive tens-transfer and one for a subtractive tens-transfer, the two mechanisms being right and left-hand images of each other. For the sake of brevity, therefore, the additive transfer mechanism will be described in detail for one order of the machine, it being understood that the subtractive tens-transfer is identical but arranged in a reverse position in regard to the accumulator gear 115.

The tens-transfer mechanism of the preferred form of my invention is shown in Fig. 2, and comprises a latch arm 1st) pivotally mounted on the tie rod 93, and rocking freely between adjacent spacing plates 91. The latch is spring-urged toward the accumulator gear 115, (counter-clockwise in Fig. 2) by a suitable spring 131 tensioned between the arm and an appropriate transverse shaft running through the separator plates. The latch arm 133 is formed to provide an abutment which engages a suitable stop in the form of a rod 132 extending transversely through the plates of the subframe assembly. A

live point 133 is pivotally mounted on the latch arm 130 by any suitable means such as rivet 134. A suitable spring 135 tensioned between the live point 133 and the latch arm 139 pulls the live point 133 (clockwise in Fig. 2) against a suitable stop pin 136 carried by the latching arm. The live point 133 is provided with a suitable cam nose 137 which cooperates with a tip of the tenstransfer cams 1117, which nose is bent to lie in the plane of the tens-transfer cam 117. It is'obvious that, when viewed from the right, as in Fig. 2, the live point 133 can yield to the passage of the tens-transfer cams mounted on the accumulator wheel 115 during rotation of the accumulator gear in the clockwise direction, but on counter-clockwise rotation of the accumulator gear the point of the tens-transfer cam 117 will cam the latch 130 clockwise away from the accumulator gear 115. The free end of the latch arm 113d is provided with a suitable latching ear 132i adapted to latch against a suitable shoulder M3 on the tens-transfer tooth.

The tens-transfer tooth is preferably shaped as a three-armed lever 140 pivotally mounted, as by pin 141, on the spring-powered bellcrank 160. The upper arm 142 of the three-armed lever 140 carries the latching shoulder 143 adapted to be engaged by the car 138 on the tens-transfer latch. The upper arm 142 is shaped at its free end to form a modified gear tooth, or pawl, L l M and is so bent that the pawl 144 lies in the next higher order of the accumulator. Adjacent the tooth 144 is a shoulder 145 adapted to engage the tie rod 99, which acts as a stop to prevent overcarry of the transfer tooth 144. The transfer tooth is so shaped that when it is held against the bar 99 by the power spring of the mechanism, the back edge of the tooth Md prevents an overthrow of the accumulator gear 115 with which the particular pawl is engaged.

A second arm 146 of the three-armed lever 140 abuts against a stop pin 147, mounted on the power bellcrank 160, thereby blocking counter-clockwise rotation of the lever 114-0. The third arm 1% of the three-armed lever is shaped as a hook on which is mounted one end of a light tension spring 149, the other end of which is hooked through an ear 161 formed on the power lever res. This permits the live tooth 140 to rock clockwise slightly when the tooth is withdrawn from engagement with accumulator gear 115 during the restoration phase of the operationthe spring M9 being light enough to allow movement of tooth or gear 115 without movement of the detent H3.

The power lever, or bellcrank, 160 is pivotally mounted on the tie rod 96. One arm carries the resiliently mounted lever 140 above described. It is also provided with a hook-like projection 162 used as a spring seat for a relatively strong spring 163 which is tensioned be tween the hook T62 of the additive transfer arm 160 and a similar hook 162a formed on the subtractive transfer arm 160a.

Thus, whenever the tens-transfer earn 117 engages the cam nose 137 of the live point 133 in additive operation (counterclockwise in Fig. 2) the latch arm 130 is rocked outwardly to release the tooth 144 of the spring-powered lever M0. The lever 160 is rocked (clockwise in Fig. 2) by its strong spring 1053 to enter a single value additively in the next adjacent accumulator gear 115.

As is particularly shown in Figs. 7, 8 and 9, a tenstransfer control cam 300 is fixed on the main drive shaft 301 of the machine and is located above, and near the left-hand end of, the accumulator assembly. This cam has a dwell portion 302, a low portion 303 and a lobe 304 arranged in arcuately consecutive relationship around the cam. A bellcrank lever 305 is pivotally mounted at one end on a pivot shaft 306 carried by the machine frame rearwardly of the accumulator assembly, and has an arm 307 extending upwardly and forwardly from the shaft 306, and has a second arm 308 extending upwardly 10 from the distal end of the arm 307 and carrying at its upper end a cam following roller 309 bearing on the peripheral edge of the cam 3120.

The shaft Edi. makes one complete rotation during each operating cycle of the machine and at the end of c cle the cam is left in the angular position, shown in Fig. '7, with the cam following roller 309 in the low portion 3 of the earn 300.

An ear 3T0 is provided on the distal end of arm 307 the bellcrank lever 305. A link 311 is pivotally conend to this ear by a rivet 312, or other i J fastener, extending through the end portion of the link and centrally through the ear 310. At its other end the link Ell is connected to the rod, or cross-member, 3270 of the tens-transfer bail, including the rod 170 and [11 ball less 1 pivotally or rockably mounted on the shaft With the cam following roller 309 in the low portion of cam 309 at the end of a machine operating cycle and at the beginning of the succeeding cycle, as shown in Pig. 7, and with the cam 30b turning in a counter-clockwise direction, as indicated by the arrows in Figs. 7, 8 and 9, shortly after the beginning of a machine operating cycle, the lobe of the cam 300 rides under the cam following roller 3d? and rocks the bellcrank lever to the maximum extent in a counter-clockwise direction, as viewed in Figs. '7, 8 and 9, to the position particularly shown in Fig. 8. This rocks the tens-transfer bail and the tens-transfer pawls 1.60 and 160a to an extent such that any pawls or levers which have been disengaged from their associated latches 130 or 130a will be relatched in inoperative position.

During the first portion of the machine operating cycle and before either of the pendent transmission gears are engaged with the accumulator drive gears 110, the roller rides ofiof the lobe 394 of the cam 300 and onto the dwell portion 3&2. This rocks the tens-transfer bail to lower the bail rod H ll to the position shown in Figs. 2 and 9 in which the rod is positioned slightly below the terminal abutment formations 164 of the spring-operated bellcrank levers and 160a. As the entry value is new read out of the differentially set actuator sectors 1?. and into the accumulator gears through the positive transmission gear train l or the negative transmission gear train 12%, and the accumulator drive gears iii), when any accumulator gear unit spaces from its 0 position, fer cam 11.7 will engage an abutment 137 at either side of the gear, dependin upon the direction of gear rotation, and force the associated latch or 130a outwardly to release the corresponding bellcrank lever 16% or a. The released bellcrank lever will then be rocked by the associated spring 2163 until the terminal abutment formation thereon engages the bail rod 170. This movement of the bellcrank lever is sufiicient to preclude accidental relatehing of the lever but is not sutlicient to impart any movement to the accumulator gear 115 coordinal with the tooth 144 of the released bellcrank lever.

The tens-transfers are thus set up during digitation but are not performed or completed until digitation is finished.

The value is read into the accumulator and the operative transmission gear train is moved away from the accumulator drive gears shortly before the end of the machine operating cycle and substantially as soon as the transmission gears have been completely disengaged from the accumulator drive gears, the cam following roller 3&9 rides off of the dwell 302 and into the low portion 303 of the cam Edit. This lowers the tens-transfer bail crossrod to the position shown in Fig. 7 and frees the unlatched pawls, or levers, 160 or 160a to advance the corresponding accumulator gears 115 one unit space in an additive or subtractive direction, as the case may be.

The tens-transfer is thus performed or completed and,

is turned through ten its associated tens-transas stated above, the tens-transfer bail is left in the position shown in Fig. 7 at the end of the cycle, this being the full-cycle position of the bail.

A subtractive transfer takes ulace in the same manner as an additive one. The mocha em, as in nti is a left-hand image of the right-hand 1 transfer mechanism described. During subtracti' erations, the accumulator gear is rotating clockwise so that upon passage of the go through the to 9 position, the tens-transfer cam ill a es th liv pawl 133a (Fig. 2) to rock the latch y, t releasing the live tooth 14911 of the subtractir sp powered lever 16%. Such release of the tens-carry arm permits the lever lfiilrt to rock slightly to engage the bail 17d and then at the end of the cycle, when the bail drops sharply, to permit the trans" r of a C i. It will be noted that the subtractive tensr levers ldtta are bent slightly so that the sh levers lie between the shoulders 164 of the additiv transfer levers.

TOTAL TAKING Totals and subtotals are readily taken in my machine during the first cycle of operation after a digitation cycle.

It will be recalled that at the end of a digitation cycle, the

actuator 11. is always restored to its normal position against the stop rod 14, in which position the printing wheel 82 will always register 0 as that wheel is always in mesh with the actuator. The theory of totalizing in my machine is to block the tens-transfer, rock the pendent gear assembly 19 to mesh with the accumulator, then operate the actuator in a down stroke which automatically subtracts the value from the accumulator gears 115. Mechanism for this purpose is shown in Fig. 2, and comprises a transverse bail 1% extending across the accumulator assembly. This bail is mounted on a pair of terminal arms 181 pivotally mounted on the tie rod 93. The bail 180 is resiliently urged away from the live pawl 133 by a suitable spring 182. Depression of a totalizing key, not shown, will operate to rock the bail 180 in front of the live pawl 133 on the tens-carry latch 139 (clockwise from the position shown in Fig. 2). Substantially, simultaneously, with the rocking of the bail 180 pendent gear train 19 is rocked so that the terminal gear 22 thereof will become enmeshed with the driving gear 110 of the accumulator assembly. Thereafter, the actuator opcrating bail is rocked downwardly, pulling the actuator 11 through the resilient connection above-described. The downward oscillation of the actuator 11, through the gear train shown, will rotate the accumulator gear 115 clockwise. When the tens-transfer cam engages the lower edge of the nose 137 of the live pawl, further rotation will be blocked by the position of the bail 18% against the top edge of the nose. The resilient connection between the power bail 50 and the actuator segment 11 will thereupon be broken and the accumulator drive gear 110, pendent gears 19, actuator 11, and the printing mechanism will thereupon remain stationary. At the end of the downstroke of the operating bail 50, the printing mechanism will be operated as above-mentioned to print the value taken out of, or transferred from, the accumulator gears, as above described. The gear train 19 is thereupon returned to its neutral, or disengaged, position (during the dwell at the end of the downstroke) and the actuator bail 50 returned to its original position-leaving the accumulator gears 115 standing at O.

Subtotals can be taken in the same way, the only change being that the pendent gears remain in mesh with the accumulator assembly at the end of the downstrolce. Thus, in subtotalizing operations, when the pendent gears 19 remain in mesh with the accumulator mechanism, the return of the actuator 11 to its zero, or full-cycle, position will operate to add back the value so taken from the accumulator during the downstroke of the actuator.

12 OPERATION It is believed that operation of the selection and accumulating mechanism of my invention has been fully explained, but it can be briefly summarized. Values are inserted into the machine through depression of the proper value keys 34 in order. As a key is depressed, it causes the elevation of the associated pin 251 and the release of the selection rack 261 by its holding pawl 269. Thus,

- the selection racks 261 are differentially set, order by order. With the setting of each rack, the carriage carrying the selection racks is stepped ordinally to the left for the insertion of the next digital value.

When appropriate operation control keys are depressed, the pendent gear trains 19 are rocked into engagement with the selection racks 261. The bail 332, mounted on the left hand carriage plate 231, engages all of the terminal gears 22 lying to the left of the leftmost rack 261, thereby blocking operation of the actuators in those higher orders. Thereafter, the actuator 11, through its poweroperated bail 50, is rocked downwardly, driving the selection racks counter-clockwise until stopped by their stop bar 268. Upon contact of the selection rack 261 with its stop bar 268, the resilient connection between the actuator segment 11 and the power-operated bail 50 is broken and the actuator comes to rest in that position.

At the end of the downstroke of the power-operated bail 50, the pendent gear train is returned to neutral position. If the value is to be added into the accumulator, the pendent gear train 19 is rocked to the other extreme position so that its terminal gear 22 will engage the driving gear of the accumulator. If, on the other hand, the value is to be subtracted from that then standing in the accumulator, the pendent gear train remains in its neutral position and the subtractive gear train is rocked to enmesh the terminal gear 126 thereof with the accumulator driving gear 110. The rocking of the gear trains to proper position occurs during a dwell at the lower end of the stroke of the power-operated bail 50.

Thereafter, the bail 50 returns to its full-cycle position and, in so doing, positively picks up the actuator 11, driving the appropriate gear train and the accumulator gear 115 a difierential amount. In the event the accumulator gear 115 passes through the 9 to 0 position, a tens-transfer takes place. In additive operation (counterclockwise in Fig. 2) the right end of the cam 117 will rock the negative live pawl 133a clockwise against the urgency of its spring. However, the opposite end of the cam 117 will engage the end of the nose 137 of the positive live pawl 133 and, as the live pawl 133 is blocked against clockwise rotation by the stop pin 136, the passage of the cam through the 9 to 0 position will rock the entire latch operatively. In subtractive operations, the gear 115 will be rotating in the opposite direction, which will rock the subtractive latch 130a outwardly and merely rock the live pawl 133 against the tension of its spring.

The releasing of the latch 130 or 130a will operate to release the spring-powered lever or 160a slightly to prevent a relatching of the latch. At the end of the cycle, the bail will rock permitting the springpowered levers 160 or 160a to drop through the pull of their spring 163. Thereupon, the tens-transfer will occur to add or subtract a value of 1 in the next higher order, and during the first portion of the succeeding cycle, the bail 170 is raised to restore the unlatched levers to their latched condition.

In totalizing or subtotalizing operations, the pendent gear train is first enmeshed with the accumulator driving gear and the blocking bail is rocked to block operation of the additive tens-transfer. Thereafter, the actuator is rocked through its power bail 50 to automatically subtract the value standing in the accumulator, which, through the gear train shown, positions the printing wheels 82 in a position corresponding to the value pre- 13 viously standing in the accumulator. This operation requires a single cycle. At the end of the downstroke of the power-operated bail 50, the printing mechanism is operated to print the total or subtotal. In a totalizing operation, the gear train 19 is rocked to a neutral position at the end of the downstroke, in the period of dwell above-mentioned. In subtotalizing operations, the gear train 19 is held in mesh with the accumulator gears so that the restoring of the actuator to its full-cycle position will add back into the accumulator gears 115 the value previously transferred therefrom into the printing Wheels.

What is claimed is:

1. In a calculating machine having differentially positionable selection racks, rockable actuator segments, a rockable operator yieldably connected to said actuator segments, movable transmission means, cyclically operating power means drivingly connected to said operator to move said actuator segments from their full-cycle position to differentially set positions and return said sectors to their full-cycle position, an accumulator having a frame fixedly mounted in said machine, drive gears and accumulator gears journalled in said frame and driven by said drive gears, and power operated means effective under manual control to move said transmission means during the former portion of an operating cycle of said power means to interconnect said selection racks and said actuator segments to read a value out of said selection racks and differentially position said actuator segments and to interconnect said actuator segments and said accumulator drive gears during the latter portion of the same operating cycle to read the value into said accumulator as said actuator segments are returned to their full-cycle position; tens-carry mechanism for said accumulator comprising a tens-carry cam mounted on and rotatable with each accumulator gear, spring-actuated pawls mounted on pivots fixed to said frame and effective when released to turn the co-ordinal accumulator gears through one unit space ineither direction, latches mounted on pivots fixed to said frame and respectively latching said pawls against gear turning movement, each latch being moved by the tens carry cam on its co-ordinal accumulator gear when such gear passes from its 9 to O or to 9 position to release the pawl associated with the accumulator gear of next higher order, pawl restoring means cooperating with said pawls and having a first position in which unlatched pawls are blocked against gear turning movement while being held in position to preclude accidental relatching thereof, a second position in which unlatched pawls are freed for gear turning movements and a third position in which the unlatched pawls are restored to latched condition, and power operated means connected to said pawl restoring means and effective to successively move said pawl restoring means from one position to another during successive operating cycles of said power means.

2. In a calculating machine having differentially positionable selection racks, rockable actuator segments, a rockable actuator yieldably connected to said actuator segments, movable transmission means, cyclically operating power means drivingly connected to said operator to move said actuator segments from their full-cycle to differentially set positions and return said segments to their full-cycle position, an accumulator having drive gears and accumulator gears driven by said drive gears, and power operated means effective under manual control to move said transmission means during the former portion of an operating cycle of said power means to interconnect said selection racks and said actuator segments to read a value out of said selection racks and differentially position said actuator segments and to interconnect said actuator segments and said accumulator drive gears during the latter portion of the same operating cycle to read the value into said accumulator as said actuator segments are returned to their full-cycle position; tens-carry mechanism for said accumulator comprising a tens-carry cam carried by each accumulator gear, spring-actuated pawls mounted on fixed pivots and disposed one at each side of each accumulator gear and effective one to turn the co-ordinal accumulator gear one unit space in one direction and the other to turn the accumulator gear one unit space in the opposite direction, latches mounted on fixed pivots one at each side of each accumulator gear and each engaging a corresponding pawl to releasably hold the pawl against gear turning movement, a live point on each latch engagecl by the tens-carry cam on the co-ordinal gear when gear passes from a 9 to 0 or a 0 to 9 position nd arranged to move the latch at one or the other side of the gear depending on the direction of gear rotation and release the corresponding pawl associated with the accumulator gear of next higher order, a bail having a first position in which it blocks the released pawls against gear turning movement but in a position in which they cannot he accidentally relatched, a second position in which it frees the unlatched pawls for gear turning movement and a third position in which it restores the unlatched pawls to latched condition, and power operated means consecutively moving said bail to said different positions during successive operating cycles of said power means.

3. In a calculating machine having differentially positionable selection racks, rockable actuator segments, a rockable operator yieldably connected to said actuator segments, movable transmission means, cyclically operating power means drivingly connected so said operator to move said actuator segments from their full-cycle to differentially set positions and return said segments to their full-cycle position, an accumulator having drive gears and accumulator gears driven by said drive gears, and power operated means effectively under manual control to move said transmission means during the former portion of an operating cycle of said power means to interconnect said selection racks and said actuator segments to read a value out of said selection racks and differentially position said actuator segments and to interconnect said actuator segments and said accumulator drive gears during the latter portion of the same operating cycle to read the value into said accumulator as said actuating segments are returned to their full-cycle position; tens-carry mechanism for said accumulator comprising a tens-carry cam carried by each accumulator gear, spring-actuated pawls mounted on fixed pivots and disposed one at each side of each accumulator gear and each effective one to turn the co-o-rdinal accumulator gear one unit space in one direction and the other to turn the accumulator gear one unit space in the opposite direction, latches mounted on fixed pivots one at each side of each accumulator gear and each engaging a corresponding pawl to releasably hold the pawl against gear turning movement, a live point on each latch engaged by the tens-carry cam on the coordinal gear when the gear passes from a 9 to 0 or a O to 9 position and arranged to move the latch at one or the other side of the gear depending on the direction of gear rotation and release the corresponding pawl associated with the accumulator gear of next higher order, a bail having a first position in which it blocks the released pawls against gear turning movement but, in a position in which they cannot be accidentally relatched, a second position in which it frees the unlatched pawls for gear turning movement and a third position in which it restores the unlatched pawls to latched condition, and power operated means consecutively moving said bail to said different positions during successive operating cycles of said power means, and blocking means pivotally mounted on fixed pivots one at each side of said accumulator gears and selectively movable into and out of position to block movement of the adjacent live tips and thereby provide means for stopping rotation of said accumulator gears in the corresponding direction at the 0 position of the gears.

4. Accumulator mechanism for a calculating machine having digitation and totalizing mechanisms and control means therefor comprising a frame adapted to be fixedly mounted in the associated calculating machine, a plurality of ordinally arranged drive gears journalled in said frame for rotation selectively in either direction by the digitation mechanism of the associated machine about a common axis fixed relative to said frame, a plurality of ordinally arranged accumulator gears journalled in said frame for rotation in either direction about a common axis fixed relative to said frame and each meshing with a corresponding drive gear for rotation thereby, spr ng actuated tens-transfer means mounted on said frame and individually engageable with said accumulator gears to selectively rotate the corresponding accumulator gears in either direction through one unit space, latch means mounted on said frame and normally engaging said tenstransfer means to hold the latter out of engagement with the corresponding accumulator gears, tens-carrying cam means mounted on each accumulator gear and effective when the associated accumulator gear has turned through a tens-transfer position to release the latch of the tens-transfer means engageable with the accumulator gear of the next higher order, means movable relative to said fixed frame for restoring said released tens-transfer means to their latched condition, means drivingly connected to said movable means for moving the latter, and stop means rigidly supported by said frame and engaged by said released sprin -actuated means when freed by said movable means to limit the gear rotating movements of said released and freed spring-actuated means.

5. Accumulator mechanism for a calculating machine having digitation and totalizing mechanisms and control means therefor comprising .a frame adapted to be mounted in the associated calculating machine, a plurality of ordinally arranged drive gears journalled in said frame for rotation selectively in either direction about a common axis by the digitation mechanism of the associated machine and for rotation in at least one direction by the totalizing mechanism of the associated machine, a plurality of ordinally arranged accumulator gears journalled in said frame for rotation in either direction about a common axis and each meshing with a corresponding drive gear for rotation thereby, spring-actuated tens-transfer means mounted on said frame and individually engageable with said accumulator gears to selectively rotate the corresponding accumulator gears in either direction through one unit space, latch means mounted on said frame and normally engaging said tens transfer means to hold the latter out of engagement with the corresponding accumulator gears, tens-carrying cam means mounted on each accumulator gear and effective when the associated accumulator gear has turned through tens-transfer position to release the latch of the tenstransfer means engageable with the accumulator gear of the next higher order, movable means effective to restore said released tens-transfer means to their latched condition, means drivingly connected to said movable means for moving the latter, and rotation limiting means disposed adjacent said latch means and movable from a position clear of said latch means to a latch engaging position to thereby render said latch means effective upon engagement of said tens-carrying cam means therewith to terminate rotation of said accumulator gears when the latter move from a set position to a position and thus condition said accumulator mechanism for the abstracting of an accumulated total therefrom by the totalizer mechanism of the associated machine.

6. An accumulator mechanism for a calculating machine comprising a frame adapted to be fixed relative to associated machine, a plurality of drive gears journalled in said frame in spaced apart relationship for rotation in either direction about a common axis fixed relative to said frame, a plurality of accumulator gears journalled in said frame in spaced apart relationship for rotation in either direction about a common axis also fixed relative to said frame and meshing each with a corresponding drive gear, spring-actuated means mounted on said frame and selectively engageable with said accumulator gears to rotate any selected accumulator gear througha unit space,latch means mounted on said frame and normally engaging said spring-actuated means to hold said spring-actuated means out of'engagement with said accumulator gears, 21 tens-carrying cam on each accumulator gear effective when the associated accumulator gear has rotated through a tens-transfer position to release lug-actuated means engageable with the accumulator gear of next higher order, movable means with which said spring-actuated means engage when said springactuated means are released to temporarily hold the released spring-actuated means out of engagement with the corresponding accumulator gears and to subsequently free said released spring-actuated means for movement into engagement with the corresponding accumulator gears to impart a rotational movement of one unit space to such gears and to return said released spring-actuated means to their latched condition, and means drivingly connected to said movable means for moving the latter.

'7. In a calculating machine having ordinal selection racks differentially settable to entry values, ordinally arranged actuator sectors rockable about a common axis, an accumulator, transmission means effective to interconnect said selection racks and said actuator sectors to differentially set said actuator sectors in accordance with the differential setting of said selection racks and to connect said actuator sectors to said accumulator to enter the value represented by the differential setting of said actuator sectors into said accumulator, an operator for rocking said actuator sectors, and means providing a releasable connection between each actuator sector and said operator, the arrangement wherein said accumulator comprises a frame fixed relative to the axis of rocking movement of said actuator sectors, ordinally arranged accumulator gears mounted in said frame for rotation about a common fixed axis parallel to the axis of said actuator sectors, accumulator drive gears mounted in said frame for rotation about a common fixed axis parallel to said accumulator gear axis and meshing co-ordinally with said accumulator gears, said transmission means being movable into engagement with said accumulator drive gears to drive the latter from said actuator sectors, a tens-transfer cam secured to and rotatable with each accumulator gear, spring-actuated pawls mounted on said frame adjacent said accumulator gears and each operative to advance the co-ordinal accumulator gear one unit space in the corresponding direction, and latches disposed one adjacent each spring-actuated pawl and each effective to latch the corresponding pawl in inoperative position until the associated latch is released by engagement therewith of the tens-transfer cam on the accumulator gear of the order next below that of the gear actuated by the particular pawl.

8. An accumulator for a calculating machine having differentially settable and ordinally arranged selection racks, ordinally arranged actuator sectors rockable about a common axis, transmission means effective to interconnect said selection racks and said actuator sectors to differentially control the rocking movements of said actuator sectors and to connect said actuator sectors to said accumulator, an operator for rocking said actuator sectors and means providing a releasable connection between each actuator sector and said operator, said accumulator comprising ordinally arranged accumulator gears rotatable about a common axis, ordinally arranged accumulator drive gears meshing respectively with said accumulator gears and engaged by said transmission means, a pair of diametrically opposed tens-transfer cams secured on each accumulator gear, a pair of latches aligned with each accumulator gear and disposed one latch at each diametrically opposite side of each gear, a spring operated pawl associated with each latch and each operative to turn an adjacent accumulator gear through one unit space in a predetermined direction when released by the corresponding latch, live tips pivotally mounted one on each latch with the live tips at one side of said gears yieldable to said tenstransfer cams when said gears are rotated in one direction and effective to trip the corresponding latches when the gears are rotated in the opposite direction and the live tips at the other sides of said gears yieldable to said tens-transfer cams when said gears are rotated in said opposite direction and effective to trip the corresponding latches when said gears are rotated in said one direction, blocking means blocking operation of the spring-actuated pawls released by the corresponding latches while said actuator sectors are connected to said accumulator drive gears, and means operating said blocking means to release said spring-actuated pawls after said accumulator drive gears have been released from said actuator sectors.

9. A calculating machine comprising positionable selection racks and means for positioning said racks, rockable actuator sectors, an oscil-latable operator for rocking said sectors, a severable connection between said operator and each of said sectors, accumulator gears, a pair of gear trains, one having an odd and the other an even number of gears therein, one train of such pair of trains being positionable to engage a said actuator sector with a said accumulator gear and the other one train of such pair of trains being positionable to engage a said actuator sector with a said selection rack or a said accumulator gear, said last-mentioned gear train being adapted to engage said selection rack during rocking of said operator in one direction and then disengaged therefrom at the end of such rocking movement, and both of said gear trains being adapted to selectively engage said accumulator gears during the return rocking of said operator, a diametrical cam member afiixed to each of said adjacent accumulator gears and lying between the and 9 positions of the respective gear, a pair of diametrically opposed latches associated with each said accumulator gear, a spring actuated member associated with each latch and operable to rotate the gear of an adjacent order for a value of 1, one of said spring-actuated members being operative in one direction and the other in the other direction, live tips on said latches, one yieldable when said accumulator gear rotates in one direction and the other when the accumulator gear rotates in the other direction, a bail normally blocking operation of said spring-actuated members, and means for operating said bail to unblock said members after the termination of digitation.

10. A reversible tens-transfer mechanism for an accumulator gear which comprises a cam member affixed to said accumulator gear and lying between the 0 and 9 positions of said gear, a pair of opposed latches associated with said gear, a spring-actuated pawl associated with each latch and operable to rotate a gear of the next higher order for a value of 1, one of said pawls being operative in one direction and the other in the opposite direction, each said latch including a live tip, one tip being yieldable when said gear rotates in one direction and the other when said gear rotates in the other direction, and pawl operating means normally blocking operation of said spring-actuated pawls and subsequently operating to unblock said pawls after the termination of digitation.

11. In an accumulator, ordinally arranged accmnulator wheels, ordinally arranged actuator wheels adapted to selectively rotate said accumulator wheels in either rotational direction, a carry cam mounted on each said accumulator wheel, spring-actuated first means to rotate each accumulator wheel one tooth in one direction, springactuated second means to rotate each accumulator wheel one tooth in the opposite direction, a first latch releasably holding said first means from rotating said wheel, a second latch releasably holding said second means from rotating said wheel, and a separate live pawl mounted on each of said latches in a position to be contacted and moved by the cam of the next lower order to release its springactuated means, said live pawls being mounted to yield in opposite directions.

12. An accumulator having denominational wheels, means for differentially stepping said wheels, a pair of wheel moving means for each wheel, one such means being operative to rotate its wheel one step in one direction and the other being operative to rotate its wheel one step in the opposite direction, a separate latch holding each said wheel moving means, a live pawl for each latch, a pawl blocking means common to the set of latches associated with the one such wheel moving means, and another pawl blocking means common to the set of latches associated with the other such wheel moving means, blocking means for both sets of said moving means, and means for removing said last-mentioned blocking means from blocking position and for thereafter returning it to blocking position.

13. In an accumulator, a plurality of ordinally arranged accumulator wheels, a carry cam secured to each wheel, spring-actuated first means to rotate each wheel separately in a first direction, spring-actuated second means to rotate each wheel separately in a second direction, a first latch releasably holding each of said first means from rotating their respective wheels, a second latch releasably holding each of said second means from rotating their respective wheels, a separate yieldable pawl mounted on each of said latches in a position to be contacted and moved by the cam of the next lower order and thereupon to release its latch from its means to rotate, said yieldable pawls being mounted to yield in opposite directions, a first blocking means common to all of said yieldable pawls associated with said first latches, a second blocking means common to all of said yieldable pawls associated with said second latches, and means for positioning said blocking means in a blocking or nonblocking position.

References Cited in the file of this patent UNITED STATES PATENTS 1,775,223 Foothorap Sept. 9, 1930 1,839,211 Foothorap Ian. 5, 1932 1,853,053 Horton Apr. 12, 1932 2,014,561 Dysart Sept. 17, 1935 2,503,865 Christian Apr. 11, 1950 UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No 2,832,544 Apr-ii 29, 1958 Harold J Chall It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

ColuxmrB, line '7, for "arm" read arms column 6, line 69, for "through" read throughout column 10, line 42, for "new" read nowfcolumn 14, line 29, for "connected so" read connected to Signed and sealed this 8th day of Ju1y 1958.

(SEAL) Attest:

KARL H. AXLINE ROBERT c. WATSON Commissioner of Patents Attesting Officer UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No 2,832,544 April 29, 1958 Harold J Chall It is herebf; certified that error appears in the printed specification of the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column?) line '7, for "arm" read arms column 6, line 69, for "through" read throughout column 10, line 42, for "new" read IIGW'Q-M; column 14, line 29; for "connected so" read connected to Signed and sealed this 8th day of July 1958.

(SEAL) Attest:

KARL H. AXLINE Attesting Ofiicer ROBERT C. WATSON Commissioner of Patents 

